EP2839173B1 - Articulation a rotule pour un véhicule - Google Patents

Articulation a rotule pour un véhicule Download PDF

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Publication number
EP2839173B1
EP2839173B1 EP13711621.6A EP13711621A EP2839173B1 EP 2839173 B1 EP2839173 B1 EP 2839173B1 EP 13711621 A EP13711621 A EP 13711621A EP 2839173 B1 EP2839173 B1 EP 2839173B1
Authority
EP
European Patent Office
Prior art keywords
ball
joint
spring
housing
pressure piece
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP13711621.6A
Other languages
German (de)
English (en)
Other versions
EP2839173A1 (fr
Inventor
Bernd Grannemann
Martin Rechtien
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2839173A1 publication Critical patent/EP2839173A1/fr
Application granted granted Critical
Publication of EP2839173B1 publication Critical patent/EP2839173B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/005—Ball joints
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G7/00—Pivoted suspension arms; Accessories thereof
    • B60G7/006—Attaching arms to sprung or unsprung part of vehicle, characterised by comprising attachment means controlled by an external actuator, e.g. a fluid or electrical motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • F16C11/0623—Construction or details of the socket member
    • F16C11/0647—Special features relating to adjustment for wear or play; Wear indicators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/10—Arrangements for locking
    • F16C11/103—Arrangements for locking frictionally clamped
    • F16C11/106—Arrangements for locking frictionally clamped for ball joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L1/00—Measuring force or stress, in general
    • G01L1/04—Measuring force or stress, in general by measuring elastic deformation of gauges, e.g. of springs
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0009—Force sensors associated with a bearing
    • G01L5/0023—Force sensors associated with a bearing by using magnetic sensors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/14—Mounting of suspension arms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/416—Ball or spherical joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2233/00—Monitoring condition, e.g. temperature, load, vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/05—Vehicle suspensions, e.g. bearings, pivots or connecting rods used therein
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/20—Joints and connections with indicator or inspection means

Definitions

  • the invention relates to a ball and socket joint for a vehicle, comprising a ball stud comprising a ball joint, a joint housing enclosing the joint ball and provided with a pin opening, in which the ball joint of the ball stud is movably mounted, wherein the ball stud extends through the pin opening out of the joint housing , And an actuator, by means of which a pressure piece in an axial direction to the joint housing is pressed, so that of the joint housing and pressure piece, a pressure on the joint ball is exercisable.
  • Such a ball joint is from the DE 197 12 947 A1 known.
  • a ball joint with a housing two arranged in the housing bearing shell elements, a pin and a ball joint having joint body sitting with its ball joint between the two bearing shell elements, and a housing bottom, which is arranged on the side facing away from the pin of the housing is.
  • an adjustable clamping device is arranged, by means of which the bias voltage with which the joint body is clamped between the bearing shell elements, is variable.
  • the tensioner may include piezoelectric or hydraulic elements, such as a hydraulic piston.
  • the friction torque can not be determined as a measured variable in every situation. Since it only occurs during relative movement of the friction partners, other sizes must be found to determine or adjust the friction torque.
  • These variables may include, for example, the path to be covered by a pressure element, the counting of revolutions of a driving electric motor, or the measurement of a motor current, by means of an evaluation unit and a calculation with the resulting friction torque is related. The primary aim of all these possibilities is to determine the axial force acting on the ball joint in order to be able to set the desired friction torque.
  • these derived variables are subject to great interference by external disturbing forces, wear in the ball joint, elasticity and friction in the system, temperature dependencies and other influences that are difficult to take into account.
  • a direct measurement of force requires sensors that are known from metrology, but for cost reasons are not accessible in large quantities (example, automotive industry).
  • the present invention seeks to provide a cost-effective way to detect the axial force.
  • the ball joint for a vehicle, in particular a motor vehicle, has a ball joint comprising a ball joint, a joint housing enclosing and provided with a pin opening hinge housing in which the ball joint ball of the ball pivot, in particular rotatable and / or pivotally mounted, is mounted, wherein the ball stud extends through the pin opening out of the joint housing out, an actuator by means of which a pressure piece in an axial direction to the joint housing to be pressed, in particular movable, so that of joint housing and pressure piece a pressure on the joint ball is exercised, a spring by means of which the actuator acts on the pressure piece, and a displacement sensor, by means of which the length of the spring is measurable.
  • the spring force can be calculated according to the Hooke's law, provided that the associated spring rate of the spring is known. This spring force corresponds in particular to the desired axial force. Since suitable springs and displacement sensors are available on the market as low-cost mass-produced goods, the combination of spring and displacement sensor forms a cost-effective force sensor.
  • the spring is arranged in the power flow between the actuator and the joint ball and / or pressure piece.
  • the spring force corresponds in particular to the axial force exerted by the pressure piece on the ball joint.
  • the actuator preferably engages axially on the pressure piece and / or on the joint ball.
  • the ball pin extends in the axial direction through the pin opening through out of the joint housing.
  • the spring rate of the spring is known.
  • a reference length of the spring and a reference force acting at the reference length are also known.
  • the length of the unloaded spring is known as the reference length.
  • the absolute length of the spring can be measured by means of the displacement sensor.
  • the length of the spring is in particular the length of the spring in the spring direction of the spring.
  • the length of the spring becomes smaller with increasing spring force and / or axial force.
  • the spring forms a compression spring.
  • the spring direction coincides with the axial direction.
  • an evaluation device coupled to the displacement sensor is provided, by means of which in particular the force exerted by the pressure piece on the joint ball and / or the force acting on the joint ball, preferably axial force, can be determined.
  • the evaluation device may be provided in or on the joint housing or at a distance therefrom.
  • the evaluation device is connected by means of electrical lines to the displacement sensor.
  • the evaluation device comprises a digital computer, in particular a microcontroller. Additionally or alternatively, however, the evaluation device may also include an analog computer.
  • the displacement sensor comprises a transmitter element and a sensor element, by means of which at least one signal emitted or deliverable by the transmitter element can be detected, which in particular supplies information about the length of the spring.
  • the signal strength and / or another property of the signal at the location of the sensor element is dependent on the distance between the transmitter element and the sensor element.
  • the donor element and the sensor element attached to the spring and have in the spring direction at a distance from each other.
  • one of the elements is connected to a coupled to the pressure piece end or connection point of the spring.
  • another of the elements is preferably connected to an actuator-coupled end or connection point of the spring.
  • the evaluation device is preferably connected to the sensor element, preferably by means of the electrical lines.
  • the transmitter element comprises a magnet, preferably a permanent magnet
  • the sensor element comprises a magnetic field-sensitive sensor, which is in particular flooded by the magnetic field of the magnet.
  • the signal is preferably by the magnetic field and / or by a characterizing the magnetic field, such. by the flux density and / or the field strength of the magnetic field.
  • the magnetic field at the location of the sensor element is dependent on the distance between the magnet and the sensor.
  • the flux density and / or the field strength of the magnetic field at the location of the sensor element is dependent on the distance between the magnet and the sensor.
  • the length of the spring can be determined.
  • the actuator is preferably coupled with the interposition of the spring with the pressure piece.
  • the spring is a spring with low hysteresis and low temperature dependence of the spring properties.
  • the spring comprises e.g. a coil spring, a plate spring, a leaf spring, a diaphragm spring or another spring known type.
  • the spring is made of metal.
  • the spring is preferably axially aligned and / or preferably extends in the axial direction.
  • the power flow through the spring in the axial direction.
  • the length of the spring in particular describes the axial extent of the spring.
  • the length of the spring is the axial length of the spring.
  • a spherical shell surrounding the joint ball is arranged in the joint housing, in which the joint ball is movable, in particular rotatable and / or pivotable, is mounted.
  • the ball socket is arranged in the axial direction between the pressure piece and a housing stop.
  • the spherical shell can form a multipart, preferably two-part spherical shell.
  • the ball shell comprises two ball shell parts, wherein a first of the ball shell parts is axially supported on the pressure piece or formed by this.
  • the first spherical shell part can be pressed by means of the actuator against the joint ball and / or displaceable relative to and / or in the joint housing, in particular in the axial direction.
  • a second of the ball shell parts is preferably axially supported on the joint housing and / or rigidly connected thereto and / or formed by this.
  • the second spherical shell part is supported axially on one or the housing stop.
  • the spherical shell parts are in particular separate parts.
  • the ball shell parts are arranged opposite one another in the axial direction.
  • the joint ball is arranged and / or enclosed in the axial direction between the ball shell parts.
  • the spherical shell forms a one-piece spherical shell.
  • the one-piece ball shell is provided with at least one slot, for example in the region of its pin opening.
  • the slot extends in the axial direction and is advantageously open to the pin opening. Through the slot, the insertion of the ball joint can be facilitated in the one-piece ball shell through the pin opening. If, as described above, a pressure exerted on the spherical shell to increase the friction torque, the slots in the axial direction cause the advantage that there is room for the elastic deformation of the spherical shell.
  • the spherical shell and / or the ball shell parts are preferably connected with respect to the axial direction in a torsionally rigid manner with the joint housing.
  • the ball socket preferably comprises an additional pin opening, through which the ball pin passes extends out of the spherical shell, in particular in the axial direction.
  • the joint housing made of metal, in particular steel.
  • the spherical shell is preferably provided with a hollow spherical bearing surface.
  • the spherical surface of the ball joint slidably abuts against the hollow spherical bearing surface.
  • the center of the hollow spherical bearing surface coincides with the center of the joint ball.
  • the spherical shell is preferably made of plastic, in particular polyacetal (POM).
  • POM polyacetal
  • each of the ball shell parts preferably comprises a part of the hollow-spherical bearing surface.
  • at least the first spherical shell part is made of plastic.
  • both ball shell parts made of plastic.
  • the plastic may be reinforced by filaments or fibers of metal or plastic.
  • the spherical shell by means of the actuator in particular with the interposition of the pressure piece, in the axial direction compressible. If the pressure piece is pressed and / or moved by means of the actuator in the axial direction onto the ball shell and / or onto the first ball shell part, then the ball shell is compressed in particular in the axial direction. In a multi-part or two-part ball shell, in particular, the ball shell parts move towards each other. In the case of a one-piece spherical shell, in particular the ball shell deforms, preferably elastically.
  • the ball shell is compressible by means of the actuator under deformation of the ball shell in the axial direction.
  • the pressure piece bears against the spherical shell and / or against the first spherical shell part.
  • the pressure piece is preferably used to initiate the spring force uniformly in the spherical shell and / or in the first spherical shell part and / or to store the spring on the spherical shell and / or on the first spherical shell part.
  • the coupled with the pressure piece end of the spring abuts against the pressure piece.
  • the transmitter element of the displacement sensor is attached to the pressure piece.
  • the spherical shell is formed conically at its outer part facing the pressure piece.
  • the pressure piece has a conical recess into which the conical outer region of the spherical shell facing the pressure piece engages.
  • the spherical shell is conically formed on its outer area facing the housing stop.
  • the housing stop preferably has a conical recess into which the conical outer region of the spherical shell facing the housing stop engages. The conical design results in particularly good force in the ball socket.
  • the ball pin preferably comprises a pin portion which is fixed, in particular rigid, connected to the ball joint.
  • the pin portion is integrally formed and / or material homogeneous with the joint ball.
  • the joint ball and the pin portion are made as separate components, which are joined together after their preparation.
  • the ball stud is preferably made of metal, in particular steel.
  • the ball stud is slidably mounted with its ball joint in a spherical shell.
  • the ball pin extends with its pin portion of the spherical shell and / or out of the joint housing.
  • the spring is introduced in particular in the power flow between the actuator and pressure piece, wherein the spring stiffness (spring rate) of the spring is known.
  • the spring is in a closed power flow with other, mostly unknown elasticities (eg joint housing, spherical shell, actuator), it can still be assumed that the spring force is equal to the sought axial force acting on the ball shell and ball joint arrangement, because it is a series of elasticities.
  • the measurement of the absolute length of the spring together with the known spring rate allows the calculation of the acting force by means of the evaluation unit.
  • the sensor element and the transmitter element of the displacement sensor are preferably coupled to the two connection points of the spring, the force determination is in particular also independent of a game, which can be adjusted by wear. Such a game is recognized, for example, as a sinking of the spring force and can be tracked by the actuator.
  • the joint housing preferably has an opening opposite the pin opening. Through this opening all, o.g. Components are introduced starting with the ball stud or the ball socket in the housing. The housing is then closed with a suitable closure.
  • lid or lock rings are suitable, which are rolled with the housing end.
  • the housing opening may have a thread at its end, so that the housing is closed with a housing cover having a corresponding mating thread. In the threaded version thus a non-destructive opening of the joint housing is possible to maintain the ball joint or individual components or to replace.
  • Fig. 1 is a schematic longitudinal section through a ball joint 1 according to a first embodiment can be seen, wherein a joint ball 2 comprehensive ball stud 3 with its ball joint 2 is rotatably and / or pivotally mounted in a spherical shell 4.
  • the ball shell 4 comprises a first ball shell part 5 and a second ball shell part 6, wherein the ball shell parts 5 and 6 rest in an axial direction 7 on different sides of the ball joint 2.
  • the second spherical shell part 6 comprises a pin opening 8, through which the ball pin 3 extends axially out of the ball socket 4.
  • the ball socket 4 is formed as a two-part ball shell, so that it is 5 and 6 microns separate components in the ball shell parts.
  • the ball socket 4 is arranged together with the ball joint 2 in a joint housing 9, which is also provided with a pin opening 10, through which the ball pin 3 extends out of the housing 9 out.
  • the ball stud 3 has a pin portion 21 which is rigidly connected to the ball joint 2.
  • the first spherical shell part 5 is displaceably guided in the axial direction 7 in the housing 9, whereas the second spherical shell part 6 is supported in the axial direction 7 on a stop 22 of the housing 9.
  • a pressure piece 11 is fixed, which is coupled with the interposition of a spring 12 with a movable part 13 of an actuator 14.
  • a stationary part 15 of the actuator 14 is fixed to the housing 9.
  • the actuator 14 is connected to a control device 16 and controlled by means of this.
  • the movable part 13 of the actuator 14 by means of the control device 16 in the axial direction 7 relative to the stationary part 15 is displaceable, so that the axial distance d between the movable part 13 and the pressure piece 11 is variable.
  • a change in the distance d but also has a change in the force exerted by the actuator 14 with the interposition of the spring 12 on the pressure member 11 in the axial direction 7 force F result.
  • the pressure element 11 transmits the force F to the first spherical shell part 5, which thus presses the joint ball 2 in the axial direction 7 against the second spherical shell part 6.
  • the current distance d corresponds to the actual length of the spring 12 and this is arranged in the power flow between the actuator 14 and spherical shell part 5, can be calculated from the length d and the spring rate of the spring 12, the force F according to the Hooke's law.
  • the spring rate is here assumed in particular as known.
  • a transmitter element 17 is fixed, which is opposite to a sensor element 18 which is mounted on a pressure member 11 facing side of the movable member 13 and has an axial distance to the transmitter element 17.
  • the transmitter element 17 is designed as a permanent magnet and the sensor element 18 as a magnetic field-sensitive sensor, which is flooded by the magnetic field of the permanent magnet.
  • a change in distance between the pressure piece 11 and the movable part 13 thus leads to a change in the magnetic field at the location of the sensor, which can be detected by means of the sensor.
  • the transmitter element 17 and the sensor element 18 together form a displacement sensor 19, by means of which the distance d can be determined.
  • the sensor element 18 is connected to an evaluation device 20 and provides this information about the distance d available, so that by means of the evaluation device 20, the force exerted by the spring 12 on the pressure pad 11 force F is calculated.
  • the spring rate of the spring 12 is stored in the evaluation device 20 as information.
  • the length of the unloaded spring 12 is preferably stored as information in the evaluation device 20.
  • the evaluation device 20 is formed by the control device 16.
  • the housing 9 is closed at its end facing away from the pin opening 10 with a lid 23 which is fixed by a formed housing edge 24 on the housing 9.
  • Fig. 2 is a schematic longitudinal section through a ball joint 1 according to a second embodiment can be seen, wherein the first embodiment, similar or identical features with the same reference numerals as in the first embodiment are designated.
  • the ball socket 4 is integrally formed and arranged in the axial direction 7 between the pressure piece 11 and the housing stop 22. The ball socket 4 is supported both on the pressure piece 11 and on the stop 22.
  • the pressure piece 11 is provided with a conical recess in which the ball socket 4 is seated with a first conical outer surface. Furthermore, the stopper 22 is provided with a conical recess in which the ball socket 4 is seated with a second conical outer surface axially opposite the first conical outer surface. Also, the housing 9 is formed in two parts and has a first housing part 25 and a second housing part 26, which is screwed to the first housing part 25 via a thread 27.
  • the second embodiment substantially coincides with the first embodiment, so that reference is made to the description of the first embodiment for further description of the second embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Pivots And Pivotal Connections (AREA)

Claims (10)

  1. Articulation à rotule pour un véhicule, comprenant un tourillon à rotule (3) comprenant une rotule d'articulation (2), un boîtier d'articulation (9) entourant la rotule d'articulation (2) et pourvu d'une ouverture de tourillon (10), dans lequel est supportée de manière déplaçable la rotule d'articulation (2) du tourillon à rotule (3), le tourillon à rotule (3) s'étendant à travers l'ouverture de tourillon (10) hors du boîtier d'articulation (9), et un actionneur (14), au moyen duquel une pièce de pression (11) peut être pressée dans une direction axiale (7) sur le boîtier d'articulation (9), de telle sorte qu'une pression puisse être exercée sur la rotule d'articulation (2) par le boîtier d'articulation (9) et la pièce de pression (11), caractérisée par un ressort (12) au moyen duquel l'actionneur (14) vient en prise sur la pièce de pression (11), et un capteur de position (19) au moyen duquel la longueur (d) du ressort (12) peut être mesurée.
  2. Articulation à rotule selon la revendication 1, caractérisée par un dispositif d'analyse (20) connecté au capteur de position (19), au moyen duquel la force (F) exercée sur la rotule d'articulation (2) par la pièce de pression (11) peut être déterminée.
  3. Articulation à rotule selon la revendication 1 ou 2, caractérisée en ce que le capteur de position (19) comprend un élément transmetteur (17) et un élément de capteur (18), au moyen duquel au moins un signal fourni par l'élément transmetteur (17) peut être détecté, lequel fournit des informations concernant la longueur (d) du ressort (12).
  4. Articulation à rotule selon la revendication 3, caractérisée en ce que l'un des éléments (17) est connecté à une extrémité du ressort (12) accouplée à la pièce de pression (11) et un autre des éléments (18) est connecté à une extrémité du ressort (12) accouplée à l'actionneur (14), de telle sorte que la distance entre les éléments (17, 18) dépende de la longueur (d) du ressort (12).
  5. Articulation à rotule selon la revendication 3 ou 4, caractérisée en ce que l'élément transmetteur (17) comprend un aimant permanent et l'élément de capteur (18) comprend un capteur sensible aux champs magnétiques, qui est parcouru par le champ magnétique de l'aimant.
  6. Articulation à rotule selon l'une quelconque des revendications précédentes, caractérisée en ce que le ressort (12) comprend un ressort à boudin, un ressort Belleville, un ressort à lame ou un ressort à membrane.
  7. Articulation à rotule selon l'une quelconque des revendications précédentes, caractérisée en ce que l'actionneur (14) est accouplé à la pièce de pression (11) par interposition du ressort (12).
  8. Articulation à rotule selon l'une quelconque des revendications précédentes, caractérisée par une coque sphérique (4) disposée dans le boîtier d'articulation (9) et entourant la rotule d'articulation (2), dans laquelle est montée de manière déplaçable la rotule d'articulation (2), la coque sphérique (4) étant disposée dans la direction axiale (7) entre la pièce de pression (11) et une butée de boîtier (22).
  9. Articulation à rotule selon la revendication 8, caractérisée en ce que la coque sphérique (4) comprend deux parties de coque sphérique (5, 6), une première des parties de coque sphérique (5) étant supportée axialement sur la pièce de pression (11) et une deuxième des parties de coque sphérique (6) étant supportée axialement sur la butée de boîtier (22) et la rotule d'articulation (2) étant disposée dans la direction axiale (7) entre les parties de coque sphérique (5, 6).
  10. Articulation à rotule selon la revendication 8, caractérisée en ce que la coque sphérique (4) est réalisée d'une seule pièce et peut être comprimée au moyen de l'actionneur (14) dans la direction axiale (7).
EP13711621.6A 2012-04-20 2013-03-19 Articulation a rotule pour un véhicule Not-in-force EP2839173B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012206537A DE102012206537A1 (de) 2012-04-20 2012-04-20 Kugelgelenk für ein Fahrzeug
PCT/EP2013/055594 WO2013156235A1 (fr) 2012-04-20 2013-03-19 Articulation sphérique pour véhicule

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EP2839173B1 true EP2839173B1 (fr) 2016-05-25

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US10696109B2 (en) 2017-03-22 2020-06-30 Methode Electronics Malta Ltd. Magnetolastic based sensor assembly
US11084342B2 (en) 2018-02-27 2021-08-10 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11135882B2 (en) 2018-02-27 2021-10-05 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11221262B2 (en) 2018-02-27 2022-01-11 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11491832B2 (en) 2018-02-27 2022-11-08 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing

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CN104033482A (zh) * 2014-06-20 2014-09-10 张宇涵 一种高压力自动示警万向节
CN104033483A (zh) * 2014-06-25 2014-09-10 无锡市崇安区科技创业服务中心 一种高压力自动示警万向节
KR102070684B1 (ko) * 2017-01-24 2020-01-29 주식회사 엘지화학 이차 전지 평가 장치
US11014417B2 (en) 2018-02-27 2021-05-25 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
CN108534734A (zh) * 2018-06-08 2018-09-14 中汽检测技术有限公司 球节测试装置及检测系统
CN109827055B (zh) * 2019-02-21 2023-11-03 安徽理工大学 一种电子产品支架
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US10696109B2 (en) 2017-03-22 2020-06-30 Methode Electronics Malta Ltd. Magnetolastic based sensor assembly
US10940726B2 (en) 2017-03-22 2021-03-09 Methode Electronics Malta Ltd. Magnetoelastic based sensor assembly
US10670479B2 (en) 2018-02-27 2020-06-02 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11084342B2 (en) 2018-02-27 2021-08-10 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11135882B2 (en) 2018-02-27 2021-10-05 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11221262B2 (en) 2018-02-27 2022-01-11 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing
US11491832B2 (en) 2018-02-27 2022-11-08 Methode Electronics, Inc. Towing systems and methods using magnetic field sensing

Also Published As

Publication number Publication date
US20150098749A1 (en) 2015-04-09
DE102012206537A1 (de) 2013-10-24
EP2839173A1 (fr) 2015-02-25
US9545828B2 (en) 2017-01-17
WO2013156235A1 (fr) 2013-10-24

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